EP2264385B1 - Cycle frigorifique et procédé d'operation d'un cycle frigorifique - Google Patents

Cycle frigorifique et procédé d'operation d'un cycle frigorifique Download PDF

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Publication number
EP2264385B1
EP2264385B1 EP10181303.8A EP10181303A EP2264385B1 EP 2264385 B1 EP2264385 B1 EP 2264385B1 EP 10181303 A EP10181303 A EP 10181303A EP 2264385 B1 EP2264385 B1 EP 2264385B1
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EP
European Patent Office
Prior art keywords
line
refrigerant
refrigeration circuit
compressor unit
collecting container
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP10181303.8A
Other languages
German (de)
English (en)
Other versions
EP2264385A3 (fr
EP2264385A2 (fr
Inventor
Bernd Heinbokel
Andreas Gernemann
Uwe Schierhorn
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Kaeltetechnik Deutschland GmbH
Original Assignee
Linde Kaeltetechnik GmbH
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Filing date
Publication date
Priority claimed from DE102004038640A external-priority patent/DE102004038640A1/de
Application filed by Linde Kaeltetechnik GmbH filed Critical Linde Kaeltetechnik GmbH
Publication of EP2264385A2 publication Critical patent/EP2264385A2/fr
Publication of EP2264385A3 publication Critical patent/EP2264385A3/fr
Application granted granted Critical
Publication of EP2264385B1 publication Critical patent/EP2264385B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

  • the invention relates to a refrigeration cycle in which a one- or multi-component refrigerant circulates, comprising in the flow direction a condenser, a collecting container, an expansion device upstream of an evaporator, an evaporator and a compressor unit.
  • the invention relates to a method for operating a refrigeration cycle.
  • liquefier should be understood to mean both liquefier and gas cooler.
  • Composite refrigerators generally supply a large number of refrigeration consumers, such as refrigerators, refrigerators and freezers. For this purpose circulates in them a one- or multi-component refrigerant or refrigerant mixture.
  • a counting of the prior art refrigeration cycle or a refrigeration system in which such a refrigeration cycle is realized, is based on the in the FIG. 1 illustrated embodiment explained in more detail.
  • the circulating in the refrigeration cycle one- or multi-component refrigerant is in a condenser or gas cooler A - hereinafter referred to only as a condenser - which is usually outside the supermarket, for example, on the roof, arranged by heat exchange, preferably against outside air, condensed.
  • the refrigerant passes through the liquid line D to the cold consumers of the so-called normal cooling circuit.
  • the in the FIG. 1 represented consumers F and F 'for any number of consumers of the normal refrigeration cycle.
  • Each of the aforementioned refrigeration consumers is preceded by an expansion valve E or E ', in which the refrigerant flowing into the refrigeration appliance or the evaporator or the evaporator of the refrigeration consumer is expanded.
  • the so-relaxed refrigerant is evaporated in the evaporators of the refrigerant consumers F and F 'and thus cools the corresponding refrigeration cabinets and rooms.
  • the refrigerant evaporated in the refrigeration consumers F and F 'of the normal refrigeration cycle is then fed via the suction line G to the compressor unit H and compressed therein to the desired pressure between 10 and 25 bar.
  • the compressor unit H is designed to be single-stage and has several compressors connected in parallel.
  • the compressed in the compressor unit H refrigerant is then fed via the pressure line I in turn to the aforementioned condenser A.
  • a second liquid line D ' is the condenser C refrigerant supplied to the condenser K and evaporated in this heat exchange with the refrigerant of the still to be explained Tiefkühlniklaufes before it is fed via the line G' of the compressor unit H.
  • the liquefied in the condenser K refrigerant of the freezing circuit is supplied via line L to the collector M of the freezing circuit.
  • the refrigerant to the consumer P - this is for any number of consumers -, which is preceded by a relaxation device O, supplied and evaporated in this.
  • the suction line Q the vaporized refrigerant is fed to the single or multi-stage compressor unit R, compressed in this to a pressure between 25 and 40 bar and then fed via the pressure line S to the aforementioned capacitor K.
  • R 404A As a refrigerant of the normal refrigeration cycle, for example, R 404A is used, while for the freezing cycle carbon dioxide is used.
  • compressor units H and R, the collector C and M and the capacitor K are usually arranged in a separate machine room.
  • about 80 to 90% of the entire pipeline network is located in the sales rooms, the storage areas or other areas of a supermarket accessible to employees and customers.
  • this line network operates at pressures of no more than 35 to 40 bar, this is acceptable to the supermarket operators both from a psychological point of view and for cost reasons.
  • Object of the present invention is to provide a generic refrigeration cycle and a method for operating a refrigeration cycle, which avoids the disadvantages mentioned.
  • a refrigeration cycle which is characterized in that between the condenser and the collecting container, an intermediate-expansion device is arranged.
  • the object is achieved in that in the intermediate between the condenser and the collecting intermediate relaxation device, a relaxation of the refrigerant to an (intermediate) pressure of 5 to 40 bar.
  • the refrigerator / refrigerator includes a liquid line for conducting liquid refrigerant separated by the gas-liquid separator to the evaporator; and a gas conduit for conducting gaseous refrigerant separated from the gas-liquid separator to an inlet side of the compressor, the gas conduit being in heat exchange with a conduit section between the outlet side of the compressor and an inlet of the condenser.
  • a refrigeration cycle, and a method for operating a refrigeration cycle and other embodiments thereof are the same below with reference to in the Figures 2 and 3 shown embodiments explained in more detail, wherein the FIG. 4 shows a refrigeration cycle according to the invention.
  • FIG. 2 a composite refrigeration system in which a possible embodiment of a refrigeration cycle is realized.
  • a procedure is described in which as a refrigerant HFC (s), HFC (s) or CO 2 can be used.
  • the compressed in the compressor unit 6 to a pressure between 10 and 120 bar refrigerant is supplied via the pressure line 7 to the condenser or gas cooler 1 and condensed in this against outside air or deprived.
  • the refrigerant is supplied to the refrigerant collector 3 via the lines 2, 2 'and 2 ", but according to the invention it is expanded in the intermediate expansion device a to an intermediate pressure of 5 to 40 bar and the collector 3 need only be designed for a lower pressure position
  • the pressure to which the refrigerant in the mentioned intermediate expansion device a is relieved is preferably selected so that it is still below the lowest expected condensing pressure.
  • the pressure line 7 with the collecting container 3, preferably with the gas space, connected or connectable can take place, for example, via a connecting line 17, in which an expansion valve h is arranged.
  • the pressure line 7 is connected or connectable to the line or line sections 2 or 2 ', 2 "connecting the condenser 1 and the collecting container 3.
  • This connection between the pressure line 7 and the line 2 or 2 ', 2 " can be done, for example, via the connecting line 18 shown in dashed lines, in which a valve j is arranged.
  • a refrigeration cycle of the collecting container 3 preferably the gas space, connected to the input of the compressor unit 6 or connectable.
  • This connection between the collecting container 3 and the input of the compressor unit 6 can, for example, via a connecting line 12, as in the FIG. 2 shown, in the suction line 11 opens, done.
  • the selected intermediate pressure can now be kept constant for all operating conditions.
  • a regulation is also possible in such a way that there is a constant difference value to the suction pressure. This ensures that the throttle steam fraction at the evaporators is comparatively small, with the result that the liquid and suction lines can be dimensioned correspondingly smaller.
  • This also applies to the condensate line, since now no gaseous components have to flow through them back into the condenser 1.
  • refrigerant is withdrawn from the collector 3 and the refrigerant consumers or their heat exchangers E2 and E3 supplied. This is preceded by a respective expansion valve b and c, in which the refrigerant flowing into the refrigeration consumer is expanded.
  • the refrigerant evaporated in the refrigeration consumers E2 and E3 is then fed back to the compressor unit 6 via the suction line 5 or sucked out of the evaporators E2 and E3 by the latter.
  • a portion of the withdrawn from the collector 3 via line 4 refrigerant is fed via line 8 to one or more frozen consumers - represented by the heat exchanger E4 -, which is also preceded by an expansion valve d supplied.
  • this partial refrigerant flow is fed via the suction line 9 to the compressor unit 10 and compressed therein to the inlet pressure of the compressor unit 6.
  • the thus compressed refrigerant partial stream is then fed via line 11 to the input side of the compressor unit 6.
  • a heat exchanger E1 can be connected upstream.
  • the heat exchanger E1 is preferably connected on the input side to the output of the condenser 1 or connectable.
  • a partial flow of the liquefied or desiccant refrigerant can now be withdrawn from the condenser or gas cooler 1 or line 2 via line 13, in which an expansion valve f is provided, and in the heat exchanger E1 against the heat exchanger E1 to be heated via line 2 'supplied refrigerant to be evaporated.
  • the vaporized refrigerant partial stream is then fed via line 14 to a compressor 6 ', which is associated with the above-described compressor unit 6 and which preferably sucks at a higher pressure level, and in this compressed to the desired final pressure of the compressor unit 6.
  • the refrigerant stream to be expanded in the intermediate expansion device a is preferably cooled to such an extent that the throttled vapor portion of the expanded refrigerant is minimized.
  • the resulting in the collector 3 throttle steam fractions can be sucked off via the line 12 and the dashed line 15 by means of the compressor 6 'at a higher pressure level.
  • FIG. 3 1 shows an embodiment of a refrigeration cycle or a method for operating a refrigeration cycle, in which the refrigerant drawn off from the collecting container 3 via the line 4 is subjected to supercooling in the heat exchanger E5.
  • the subcooling takes place - in accordance with an advantageous embodiment - in heat exchange with the flash gas withdrawn from the collecting container 3 via line 12.
  • Liquid lines such as those in the Figures 2 and 3 shown line 4, with a temperature level below the ambient temperature exposed to heat radiation. This has the consequence that the refrigerant flowing inside the liquid line partially evaporates, thus resulting in the formation of undesirable vapor contents.
  • refrigerants are previously undercooled either by an expansion of a partial flow of the refrigerant and subsequent evaporation or by an internal heat transfer to a suction gas stream, which is thereby overheated.
  • the temperature difference between the suction and liquid line or the circulating refrigerant therein may be too low to realize an internal heat transfer for the required supercooling of the refrigerant flowing in the liquid line.
  • the procedure described thus has the additional advantage that the reliability of the compressor or compressor unit 6 is increased due to a safe overheating of the flash gas stream.
  • FIG. 4 shows an embodiment of the refrigeration cycle according to the invention or the method according to the invention for operating a refrigeration cycle. For the sake of clarity is in the FIG. 4 only a part of the in the FIG. 2 and 3 shown refrigerant circuit shown.
  • the method according to the invention for operating a refrigeration cycle further develops that at least a partial flow of the flash gas withdrawn from the collecting container is at least temporarily overheated against at least a partial flow of the compressed refrigerant.
  • FIG. 4 shows a possible embodiment of the method according to the invention, in which at least temporarily a partial flow of the withdrawn from the reservoir 3 via line 12 flash gas via line 16 to a heat exchanger E6 and superheated in this against the compressed in the compressor unit 6 refrigerant.
  • the flash gas stream After passing through the heat exchanger / superheater E6, the flash gas stream is supplied via line 16 'to the inlet of the compressor 6' of the compressor unit 6.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Transmitters (AREA)
  • Details Of Measuring And Other Instruments (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)

Claims (14)

  1. Cycle frigorifique, dans lequel un agent réfrigérant à un ou plusieurs composants, en particulier du CO2, circule, dans lequel le cycle frigorifique permet une opération supercritique, présentant dans le sens d'écoulement un condenseur/refroidisseur de gaz (1), un dispositif de détente intermédiaire (a), un récipient de collecte (3), un dispositif de détente (b, c) monté en amont d'un évaporateur (E2, E3), un évaporateur (E2, E3) et une unité compresseur (6) reliée à l'évaporateur (E2, E3) par une conduite d'aspiration (5), dans lequel l'unité compresseur (6) est reliée au condenseur/refroidisseur de gaz (1) au moyen d'une conduite de pression (7), dans lequel la chambre à gaz du récipient de collecte (3) est reliée ou peut être reliée à l'entrée de l'unité compresseur (6) par le biais d'une conduite (12, 16), caractérisé en ce qu'un échangeur de chaleur (E6) est prévu, auquel un flux partiel du gaz flash prélevé du récipient de collecte (3) par le biais de la conduite (12, 16) est amené au moins temporairement et dans lequel ce flux partiel est surchauffé contre l'agent réfrigérant comprimé dans la conduite de pression (7).
  2. Cycle frigorifique selon la revendication 1, dans lequel le gaz flash après passage par l'échangeur de chaleur/surchauffeur (E6) est amené à l'entrée du compresseur (6') de l'unité compresseur (6) par le biais d'une conduite (16').
  3. Cycle frigorifique selon la revendication 1 ou 2, dans lequel un échangeur de chaleur (E1) est monté en amont du récipient de collecte (3).
  4. Cycle frigorifique selon la revendication 3, dans lequel l'échangeur de chaleur (E1) est relié ou peut être relié (2, 13) côté entrée à la sortie du condenseur/refroidisseur de gaz (1).
  5. Cycle frigorifique selon la revendication 3 ou 4, dans lequel la conduite (2) du condenseur/refroidisseur de gaz (1) se divise en une première section de conduite (2') et en une deuxième section de conduite (13), dans lequel une soupape de détente (f) est agencée dans la deuxième section de conduite (13), et dans lequel l'agent réfrigérant dans la deuxième section de conduite (13) est évaporé dans l'échangeur de chaleur (E1) contre l'agent réfrigérant dans la première section de conduite (2').
  6. Cycle frigorifique selon la revendication 5, dans lequel la deuxième section de conduite (13, 14) est reliée ou peut être reliée à l'entrée du compresseur (6') de l'unité compresseur (6) après l'échangeur de chaleur (E1).
  7. Cycle frigorifique selon la revendication 5 ou 6, dans lequel la conduite de pression (7) est reliée ou peut être reliée à la conduite (2, 2', 2'') reliant le condenseur/refroidisseur de gaz (1) et le récipient de collecte (3).
  8. Cycle frigorifique selon l'une quelconque des revendications 5 à 7, dans lequel la conduite (18) avec une soupape (j), qui y est prévue, relie la première section de conduite (2') après l'échangeur de chaleur (E1) à la conduite de pression (7) après l'unité compresseur (6).
  9. Cycle frigorifique selon l'une quelconque des revendications précédentes, dans lequel la conduite de pression (7) est reliée ou peut être reliée au récipient de collecte (3), de préférence à sa chambre à gaz.
  10. Cycle frigorifique selon la revendication 9, dans lequel une soupape de détente (h) est prévue dans la conduite (17), qui relie la conduite de pression (7) au récipient de collecte (3).
  11. Cycle frigorifique selon l'une quelconque des revendications précédentes, dans lequel l'agent réfrigérant prélevé du récipient de collecte (3) est amené par le biais d'une conduite (8) à un ou plusieurs consommateurs de congélation (E4), auxquels une soupape de détente (d) est montée en amont.
  12. Cycle frigorifique selon la revendication 11, dans lequel une unité compresseur (10) est prévue, qui est alimentée en agent réfrigérant évaporé dans le consommateur de congélation (E4) par le biais d'une conduite d'aspiration (9), et dans lequel l'agent réfrigérant comprimé dans l'unité compresseur (10) est amené à l'unité compresseur (6) par le biais d'une conduite d'aspiration (11).
  13. Procédé d'opération d'un cycle frigorifique, dans lequel un agent réfrigérant à un ou plusieurs composants, en particulier du CO2, circule dans le sens d'écoulement à travers un condenseur/refroidisseur de gaz (1), un dispositif de détente intermédiaire (a), un récipient de collecte (3), un dispositif de détente (b, c) monté en amont d'un évaporateur (E2, E3), un évaporateur (E2, E3) et une unité compresseur (6) reliée à l'évaporateur (E2, E3) par une conduite d'aspiration (5), dans lequel du gaz flash est amené de la chambre à gaz du récipient de collecte (3) à l'entrée de l'unité compresseur (6) par le biais d'une conduite (12, 16), caractérisé en ce que dans le dispositif de détente intermédiaire (a) agencé entre le condenseur/refroidisseur de gaz (1) et le récipient de collecte (3), une détente de l'agent réfrigérant à une pression intermédiaire de 5 à 40 bar a lieu, et un flux partiel du gaz flash (12, 16) prélevé du récipient de collecte (3) est surchauffé (E6) au moins temporairement contre l'agent réfrigérant (7) comprimé dans la conduite de pression (7), qui relie l'unité compresseur (6) au condenseur/refroidisseur de gaz (1).
  14. Procédé selon la revendication 13, dans lequel l'agent réfrigérant (2) est refroidi avant sa détente intermédiaire (a).
EP10181303.8A 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique Expired - Lifetime EP2264385B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004038640A DE102004038640A1 (de) 2004-08-09 2004-08-09 Kältekreislauf und Verfahen zum Betreiben eines Kältekreislaufes
EP05775838A EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP05775838.5 Division 2005-07-29
EP05775838A Division EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique

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EP2264385A2 EP2264385A2 (fr) 2010-12-22
EP2264385A3 EP2264385A3 (fr) 2011-10-19
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EP05723393A Expired - Lifetime EP1794510B1 (fr) 2004-08-09 2005-02-18 Circuit de réfrigération à co2 avec sous-refroidissement de l'agent réfrigérant liquide contre la vapeur instantanée de la bouteille accumulatrice et méthode pour exploiter celui-ci
EP05715407.2A Expired - Lifetime EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP10167202.0A Expired - Lifetime EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP10181303.8A Expired - Lifetime EP2264385B1 (fr) 2004-08-09 2005-07-29 Cycle frigorifique et procédé d'operation d'un cycle frigorifique
EP05775838A Expired - Lifetime EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique
EP07020311.2A Expired - Lifetime EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique

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EP05723393A Expired - Lifetime EP1794510B1 (fr) 2004-08-09 2005-02-18 Circuit de réfrigération à co2 avec sous-refroidissement de l'agent réfrigérant liquide contre la vapeur instantanée de la bouteille accumulatrice et méthode pour exploiter celui-ci
EP05715407.2A Expired - Lifetime EP1782001B1 (fr) 2004-08-09 2005-02-18 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant
EP10167202.0A Expired - Lifetime EP2244040B1 (fr) 2004-08-09 2005-07-29 Vidange de vapeur instantanée du réservoir d'un circuit refrigérant

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EP05775838A Expired - Lifetime EP1789732B1 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procede de fonctionnement d'un circuit frigorifique
EP07020311.2A Expired - Lifetime EP1895246B3 (fr) 2004-08-09 2005-07-29 Circuit frigorifique et procédé de fonctionnement d'un circuit frigorifique

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EP (6) EP1794510B1 (fr)
KR (2) KR20070050046A (fr)
CN (3) CN100507402C (fr)
AT (1) ATE544992T1 (fr)
AU (2) AU2005278162A1 (fr)
DK (4) DK1794510T3 (fr)
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DK1895246T3 (da) 2017-03-06
KR20070050046A (ko) 2007-05-14
EP1789732A1 (fr) 2007-05-30
DK2264385T3 (en) 2018-07-23
DK2244040T3 (da) 2019-12-02
WO2006022829A1 (fr) 2006-03-02
KR20070046847A (ko) 2007-05-03
HK1144011A1 (en) 2011-01-21
EP2264385A3 (fr) 2011-10-19
US7644593B2 (en) 2010-01-12
EP1782001B1 (fr) 2016-11-30
CN100582603C (zh) 2010-01-20
DK1895246T6 (da) 2019-06-11
AU2005270472B2 (en) 2011-01-06
EP1895246B3 (fr) 2018-05-02
CN101713596A (zh) 2010-05-26
DK1794510T3 (da) 2012-05-21
AU2005278162A1 (en) 2006-03-02
RU2007107807A (ru) 2008-09-20
EP2244040B1 (fr) 2019-08-28
WO2006022829A8 (fr) 2007-03-22
EP1794510A1 (fr) 2007-06-13
CN101014815A (zh) 2007-08-08
EP2244040A2 (fr) 2010-10-27
NO20071229L (no) 2007-03-06
EP2244040A3 (fr) 2011-10-12
HK1101199A1 (en) 2007-10-12
CN101040153A (zh) 2007-09-19
CN101713596B (zh) 2012-08-08
CN100507402C (zh) 2009-07-01
ATE544992T1 (de) 2012-02-15
EP1794510B1 (fr) 2012-02-08
EP1895246A3 (fr) 2009-02-11
US20080104981A1 (en) 2008-05-08
EP1895246A2 (fr) 2008-03-05
EP1789732B1 (fr) 2011-03-23
EP2264385A2 (fr) 2010-12-22
US20080078203A1 (en) 2008-04-03
AU2005270472A1 (en) 2006-02-16
EP1782001A1 (fr) 2007-05-09
NO343330B1 (no) 2019-02-04
US8113008B2 (en) 2012-02-14
EP1895246B1 (fr) 2016-11-23
RU2362096C2 (ru) 2009-07-20

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